EP2022975B1 - Injecteur - Google Patents

Injecteur Download PDF

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Publication number
EP2022975B1
EP2022975B1 EP08104407A EP08104407A EP2022975B1 EP 2022975 B1 EP2022975 B1 EP 2022975B1 EP 08104407 A EP08104407 A EP 08104407A EP 08104407 A EP08104407 A EP 08104407A EP 2022975 B1 EP2022975 B1 EP 2022975B1
Authority
EP
European Patent Office
Prior art keywords
control valve
duct
injector
control
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08104407A
Other languages
German (de)
English (en)
Other versions
EP2022975A1 (fr
Inventor
Hans-Christoph Magel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2022975A1 publication Critical patent/EP2022975A1/fr
Application granted granted Critical
Publication of EP2022975B1 publication Critical patent/EP2022975B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • An injector for injecting fuel into a combustion chamber of an internal combustion engine in which a nozzle needle is exposed to a rear control surface of a control chamber.
  • the control chamber is permanently connected to the high-pressure region of a common rail via an inlet throttle channel.
  • the control chamber is associated with a control valve which connects a combined inlet and outlet throttle channel in a first switching position for closing the nozzle needle with the high pressure region and in a second switching position closes a sealing seat to the high pressure region and at the same time opens a sealing seat to the low pressure region.
  • An injector for injecting fuel with a 4/2-way valve for driving a nozzle needle goes out US 7111614 B1 out.
  • the hydraulic connection of a pressure chamber of the nozzle needle is switched to the high pressure region of the 4/2-way valve.
  • the same control valve switches an inlet throttle channel to a control chamber in the first switching position for opening the nozzle needle to a low-pressure region and in the second switching position for closing the nozzle needle to the high-pressure region towards free.
  • an injector which has an actuatable with an electromagnetic actuator control valve.
  • the control valve has an adjustable between two switching positions valve member, wherein in a first switching position of the control valve, a throttle-free inlet channel is hydraulically connected to a throttle-free vomichkanal, which in turn opens into a control chamber which is bounded by an end face of the valve element. In this way, a fast, throttle-free refilling of the control chamber and thus a fast closing behavior of the valve element of the injector can be achieved.
  • the invention has for its object to provide an injector, are minimized in the pressure oscillations in the control chamber with simultaneous realization of a fast valve element closing movement.
  • the invention is based on the idea that a backfilling channel is provided, which leads from the control valve into the control chamber, wherein in the first switching position of the control valve the backfill channel is hydraulically connected to the inlet channel, then that fuel from the high-pressure region via the inlet channel, the control valve and the rinse vorllkanal can flow into the control chamber, and that the connection between the remind spallkanal and the inlet channel is blocked in the second switching position of the control valve.
  • Theradyogllkanals is thereby activated by the control valve, that is, activated by a valve member of the control valve, such that the connection between the remind sympatuent and the inlet channel is blocked in the second switching position of the control valve and opened in the first switching position for fast refilling of the control chamber.
  • the concept of the invention can be implemented both in an injector with an electromagnetic actuator and in an injector with a piezoelectric actuator or with an actuator having a different principle of action.
  • the map slope, especially at high system pressures is reduced by, in addition to the rinse pump the inlet throttle channel is provided, which connects the control chamber - permanently - with the high pressure area.
  • the vibrations in the servo circuit are further reduced.
  • the opening speed of the valve element in a simple manner by adjusting the ratio of the flow cross-sections of the inlet throttle channel be tuned to the outlet throttle channel.
  • the inlet throttle channel can be branched off, for example, from a supply channel in the injector, which supplies a pressure chamber with high-pressure fuel.
  • an inlet throttle channel directly between the pressure chamber and the control chamber, wherein the inlet throttle channel, for example, in a sleeve-shaped, the control chamber radially outwardly limiting component is introduced.
  • the control valve comprises a valve member that is adjustable in particular in the axial direction, by the adjustment of which the at least two, preferably only two switching positions of the control valve are realized.
  • the valve member is in the first switching position, in which the inlet channel is open and the control chamber is connected via the inlet channel and the vomyogllkanal to the high pressure region, at a first control valve seat and in the second switching position at a second, the first control valve seat preferably axially opposed control valve seat ,
  • the two control valve seats identical or preferably different form, with at least one of the control valve seats is designed as a flat seat, conical seat, ball seat or slide edge.
  • the outlet throttle channel is arranged in the fuel flow direction between, preferably axially between the control chamber and the first control valve seat, so that the fuel at the second control valve seat fitting valve member (second switching position) from the control chamber to the first control valve seat and from there into the low-pressure area and the injector return can flow.
  • the outlet throttle channel is arranged in the direction of fuel flow behind the first control valve seat, so that the fuel can flow from the control chamber to the first control valve seat and past it through the outlet throttle channel into the low-pressure region and thus to the injector return in the case of the second control valve seat.
  • the inlet channel is provided with a throttle.
  • the valve element closing speed can be tuned improved.
  • a restriction may be provided in the inlet to the valve seat of the valve element, for example in the valve element guide, in order to improve the closing behavior of the valve element. If such a throttle is dispensed with, the effective injection pressure can be increased.
  • the provision of a throttle in the inlet channel improves the tolerance sensitivity of the injector.
  • control valve is designed as a valve pressure-balanced in the axial direction.
  • a pressure-balanced control valve One possibility for realizing a pressure-balanced control valve is that a preferably centric axial passage is provided in the valve member, through which the fuel in the second switching position can flow into the low-pressure region, wherein at befindlichem in the first switching position control valve, ie at the first control valve seat abutting valve member bears against both ends of the valve member low pressure and the guide diameter of the valve member are at least approximately identical.
  • Fig. 1 is shown very schematically the structure of an injector 1 designed as a common rail injector.
  • the injector 1 is supplied via a high-pressure supply line 2 from a fuel high-pressure accumulator 3 (rail) with fuel at high pressure (preferably higher than 2000 bar), in particular diesel oil or gasoline.
  • the high-pressure supply line 2 preferably continues within the injector as a supply channel.
  • the fuel high-pressure accumulator 3 is supplied with fuel from a low-pressure reservoir 5 by a high-pressure pump 4 designed as a radial piston pump.
  • a low-pressure region 6 of the injector 1 is hydraulically connected via a return 7 to the reservoir 5.
  • the pressure in the low-pressure region 6 of the injector 1 is between about 0 and 100 bar, preferably between about 0 and 10 bar.
  • a fuel quantity to be explained later (control amount) is discharged from a control chamber 8 and fed back to the high-pressure circuit via the high-pressure pump 4.
  • a one-piece valve element 10 in this embodiment is arranged within a belonging to a high-pressure region of the injector 1 pressure chamber 9, a one-piece valve element 10 in this embodiment is arranged.
  • a multi-part, in particular two-part design of the valve element 10, in particular with control rod and nozzle needle conceivable.
  • the control chamber 8 Radially outward, the control chamber 8 is bounded by a sleeve 12, which is pressed by a closing spring 13 in the axial direction against a throttle plate 14.
  • the closing spring 13 is supported a circumferential collar 15 of the valve element 10 and acts on this in the direction of its valve seat 16th
  • valve member 10 When the valve member 10 abuts the valve seat 16, i. is in a closed position, the fuel outlet from a nozzle hole arrangement 17 in a combustion chamber (not shown) of the internal combustion engine is locked. If, on the other hand, it is lifted from the valve seat 16, fuel can flow from the pressure chamber 9 via axial channels 18, which are formed by a polygonal contoured guide section 19 of the valve element 10, past the valve seat 16 to the nozzle hole arrangement 17 and from there into the combustion chamber (not shown). It is conceivable to form the axial channels 18 as throttle channels.
  • a control valve 20 associated with the control chamber 20 (servo valve) is moved by means of an actuator 21 from a first switching position to a second switching position, wherein in the second switching position a branched off from the high-pressure supply line 2 inlet channel 22 with throttle 23 (alternatively throttle-free) is locked, so that the hydraulic connection between the high-pressure region of the injector 1 and the control chamber 8 is interrupted.
  • the throttle 23 in the inlet channel 22 is substantially larger than the inlet throttle 27.
  • the flow cross-sections of the inlet throttle 27 and the outlet throttle 25 are matched to one another in such a way that when befindlichem in the second switching position Control valve 20, a net outflow of fuel from the control chamber 8 results and as a result, the pressure in the control chamber 8 decreases and thus the valve element 10 lifts from its valve seat 16 in the plane of the drawing and thus the fuel flow from the pressure chamber 9 into the combustion chamber of the internal combustion engine releases.
  • the control valve 20 is transferred from the second switching position to the first switching position, in which a throttle-free vomichkanal 28, which leads from the control valve 20 into the control chamber 8 is hydraulically connected to the inlet channel 22, so that fuel from the high-pressure region via the inlet channel 22, the control valve 20 and the remind Stahlllkanal 28 can flow into the control chamber 8, whereby the pressure in the control chamber 8 increases rapidly.
  • the pressure increase of the control chamber 8 is assisted by the flowing into the control chamber 8 through the inlet throttle 26 fuel.
  • it is also an embodiment of the injector 1 without inlet throttle channel 26 can be realized.
  • the hydraulic connection of the control chamber 8 to the low-pressure region 6, ie the outlet throttle channel 24 is blocked, so that no fuel can flow into the low-pressure region 6.
  • the inlet throttle channel 26 is arranged in the flow direction between the control chamber 8 and the control valve 20.
  • the backfill channel 28 itself is not switched, but only the inlet channel 22, wherein also an embodiment with switchable backfill channel 28 can be realized.
  • FIG. 2 an alternative embodiment of an injector 1 is shown, which largely corresponds to the embodiment according to Fig. 1 corresponds, so that to avoid repetition essentially only to the differences from the embodiment according to Fig. 1 will be received.
  • the essential difference from the embodiment according to Fig. 1 consists in that the outlet throttle channel 24 with outlet throttle 25 is arranged downstream of the control valve 20, more precisely the control valve seats of the control valve 20.
  • a drain channel 29 is provided between the control chamber 8 and the control valve 20, by the fuel in the second switching position of the control valve 20 to the outlet throttle channel 24 and from there to the low pressure region 6 and 7 can flow to the return. It is conceivable that in the first switching position of the control valve 20 only the outlet throttle channel 24 is switched or additionally or alternatively the drain channel 29th
  • FIG. 3 is a structurally concrete possible embodiment of an injector 1 shown.
  • An essential part of the injector 1 is the control valve 20 with its elongated, piston-shaped valve member 30 which is fixedly formed with an armature plate 31 of the electromagnetic actuator 21 in this embodiment.
  • the valve member 20 is spring-loaded by a compression spring 32 in the direction of its first, formed as a flat seat control valve seat 33.
  • the valve member 30 is adjustable between the first control valve seat 33 and an opposing second, inner conical control valve seat 34. To adjust the valve member 30 of the first control valve seat 33 (first switching position) to rest on the second control valve seat 34 (second switching position) of the electromagnetic actuator 21 must be energized, whereas the energization is interrupted for returning to the first switching position.
  • Fig. 3 the first switching position of the valve member 30 is shown.
  • the valve member 30 abuts against its first control valve seat 33, whereby the connection of the control chamber 8 to the low-pressure region 6 and thus to the return line 7 is interrupted.
  • the over the high pressure supply line 2 and the supply channel 39 into the pressure chamber 9 flowing fuel passes through the throttle in this embodiment formed inlet channel 22 into a valve chamber 35 of the control valve 20 and from there via the remindzellkanal 28 in the control chamber 8, the same time permanently on the Inlet throttle 26 with inlet throttle 27 with the pressure chamber 9 (high pressure area) of the injector 1 is connected.
  • the inlet throttle channel 26 is introduced into a sleeve-shaped component 36 as a radial bore, wherein the sleeve-shaped member 36, the control chamber 8 the frontally delimiting valve member 10 leads and radially outwardly and axially upwardly bounds the control chamber 8.
  • the control chamber 8 is brought quickly to system pressure, so that the valve element 10 moves in the plane of the drawing down on its valve seat 16 and the nozzle hole assembly 17 is blocked in the sequence.
  • valve element 10 To open the nozzle hole arrangement 17, the valve element 10 must be moved upwards in the plane of the drawing, for which purpose the pressure in the control chamber 8 has to be lowered.
  • the electromagnetic actuator 21 is energized, whereby the valve member 30 moves upwards in the plane of the drawing and comes to bear against the second control valve seat 34.
  • the connection of the inlet channel 22 to the valve chamber 35 and thus to the backfill channel 28 and the control chamber 8 is interrupted.
  • valve member 30 since the valve member 30 is no longer applied to its first control valve seat 30, fuel from the control chamber 8 via the outlet throttle channel 24 with outlet throttle 25 in an intermediate chamber 37 radially outside the first control valve seat 33 and from there to the first control valve seat 33 passing by a Axialkanal 38 within the valve member 30 through the low pressure region 6 and thus to the return flow 7. As a result, the pressure in the control chamber 8 decreases and the valve element 10 lifts off from its valve seat 16, so that the injection process begins. In the switching phases of the control valve 20, there are (almost) no short circuit losses due to simultaneously open control valve seats, since both control valve seats 33, 34 are hydraulically connected to one another only via the outlet throttle channel 24 with outlet throttle 25.
  • Fig. 3 how out Fig. 3 can be seen, it is in the control valve 20 is a pressure balanced in the axial direction valve. This is achieved in that a first guide diameter D 1 and an axially spaced guide diameter D 2 of the valve member 30 are the same size and thus act in the two opposite axial directions with low pressure surfaces of the valve member 30 are equal.
  • throttling can be provided, for example in the region of the axial channels 18. Furthermore, a throttle can be provided in the inlet channel 22.
  • control valve seats 33,34 are arranged in a portion 40 of the injector 1, which projects into the pressure chamber 9 and thus is surrounded by fuel under high pressure.
  • control valve seats 33,34 are arranged in different chambers, namely the first control valve seat 33 in the valve chamber 35 and the second control valve seat 34 in the intermediate chamber 37, wherein the valve chamber 35 and the intermediate chamber 37 only via the outlet throttle channel 24th connected to a smaller flow area. Axially between the valve chamber 35 and the intermediate chamber 37, a guide portion for the valve member 30 is provided.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (9)

  1. Injecteur pour injecter du carburant dans une chambre de combustion d'un moteur à combustion interne, en particulier injecteur à rampe commune, comprenant un élément de soupape (10) déplaçable en fonction de la pression de carburant dans une chambre de commande (8) entre une position de fermeture et une position d'ouverture libérant le flux de carburant et comprenant une soupape de commande (20) associée à la chambre de commande (8), qui est reliée par le biais d'un canal d'afflux (22) à une région de haute pression de l'injecteur (1), un canal d'étranglement de sortie (24) et un canal d'étranglement d'amenée (26) reliant la chambre de commande (8) de manière durable avec la région à haute pression étant prévus, le canal d'amenée (22) étant ouvert dans une première position de commutation de la soupape de commande (20) et la chambre de commande (8) étant connectée à la région à haute pression de l'injecteur (1), et la chambre de commande (8) étant séparée d'une région à basse pression (6), et dans une deuxième position de commutation de la soupape de commande (20), le canal d'amenée (22) étant bloqué et la chambre de commande (8) étant connectée à la région à basse pression (6) par le biais du canal d'étranglement de sortie (24), caractérisé en ce qu'il est prévu un canal de retour (28) qui conduit de la soupape de commande (20) dans la chambre de commande (8), et en ce que dans la première position de commutation de la soupape de commande (20), le canal de retour (28) est connecté hydrauliquement au canal d'amenée (22) et dans la deuxième position de commutation de la soupape de commande (20), la connexion entre le canal de retour (28) et le canal d'amenée (22) est bloquée.
  2. Injecteur selon la revendication 1, caractérisé en ce que la soupape de commande (20) présente un organe de soupape réglable, en particulier axialement (30), qui, dans la première position de commutation, s'applique contre un premier siège de soupape de commande (33) et dans la deuxième position de commutation s'applique contre un deuxième siège de soupape de commande (34).
  3. Injecteur selon la revendication 2, caractérisé en ce que le canal d'étranglement de commande (24) est disposé dans la direction d'écoulement du carburant entre la chambre de commande (8) et le premier siège de soupape de commande (33).
  4. Injecteur selon la revendication 2, caractérisé en ce que le canal d'étranglement de sortie (24) est disposé dans la direction d'écoulement du carburant derrière le premier siège de soupape de commande (33).
  5. Injecteur selon la revendication 1, caractérisé en ce que le canal d'amenée (22) est réalisé sous forme de canal d'étranglement.
  6. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que la soupape de commande (20) est réalisée sous forme de soupape équilibrée en pression, dans la direction axiale, au moins approximativement.
  7. Injecteur selon la revendication 2, caractérisé en ce que dans l'organe de soupape (30) est prévu un canal axial (38), par le biais duquel du carburant s'écoule dans la deuxième position de commutation de la soupape de commande (20) dans la région à basse pression (6).
  8. Injecteur selon l'une quelconque des revendications 2 à 7, caractérisé en ce que les sièges de soupapes de commande (33, 34) sont disposés dans une portion (40) de l'injecteur (1), qui est entourée radialement à l'extérieur par du carburant sous haute pression.
  9. Injecteur selon l'une quelconque des revendications 2 à 8, caractérisé en ce que les deux sièges de soupapes de commande (33, 34) sont disposés dans des chambres différentes, entre lesquelles de préférence une portion de guidage pour l'organe de soupape (30) est prévue, et qui sont de préférence connectées l'une à l'autre uniquement par le canal d'étranglement de sortie (24).
EP08104407A 2007-07-24 2008-06-13 Injecteur Not-in-force EP2022975B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007034319A DE102007034319A1 (de) 2007-07-24 2007-07-24 Injektor

Publications (2)

Publication Number Publication Date
EP2022975A1 EP2022975A1 (fr) 2009-02-11
EP2022975B1 true EP2022975B1 (fr) 2010-05-12

Family

ID=39929850

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08104407A Not-in-force EP2022975B1 (fr) 2007-07-24 2008-06-13 Injecteur

Country Status (3)

Country Link
EP (1) EP2022975B1 (fr)
AT (1) ATE467757T1 (fr)
DE (2) DE102007034319A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2615294A1 (fr) 2012-01-13 2013-07-17 Delphi Technologies Holding S.à.r.l. Injecteur à carburant
DE102012005319A1 (de) * 2012-03-19 2013-09-19 L'orange Gmbh Injektorbaugruppe
DE102017103082A1 (de) 2017-02-15 2018-03-15 L'orange Gmbh Kraftstoff-Einspritzinjektor für eine Brennkraftmaschine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19533786B4 (de) 1995-09-13 2004-02-12 Robert Bosch Gmbh Magnetventil zur Steuerung von Druckmedien
DE10131618A1 (de) * 2001-06-29 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit zuschaltbarem Steuerraumzulauf
DE102004015744A1 (de) * 2004-03-31 2005-10-13 Robert Bosch Gmbh Common-Rail-Injektor
US7111614B1 (en) 2005-08-29 2006-09-26 Caterpillar Inc. Single fluid injector with rate shaping capability
US7415969B2 (en) * 2006-02-28 2008-08-26 Caterpillar Inc. Fuel injector having recessed check top
DE102006036446A1 (de) 2006-08-04 2008-02-07 Robert Bosch Gmbh Injektor für ein Kraftstoffeinspritzsystem
DE102006056840A1 (de) * 2006-12-01 2008-06-05 Robert Bosch Gmbh Kraftstoffinjektor

Also Published As

Publication number Publication date
DE502008000639D1 (de) 2010-06-24
EP2022975A1 (fr) 2009-02-11
DE102007034319A1 (de) 2009-01-29
ATE467757T1 (de) 2010-05-15

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